Tractor loaders



Nov. 29, 1960 T. G. GRANRYD TRACTOR LoADERs 'Y 16 Sheets-Sheet 1V Original Filed Sept. l0, 1956 JNVENTOR.

EVP C). Q

Nov. 29, 1960 T. G. GRANRYD 2,961,889

TRACTOR LOADERS Original Filed Sept. 10. 1956 16 Sheets-Sheet 2 INVENTORI. Wem/2;@

QMQ O 5% Nov. 29, 1960r T. G. GRANRYD 2,961,889

TRACTOR LoADERs originaliled sept. 1o, 1956 16 sheets-sneet s NOV- 29, 1960 T. G. GRANRYD 2,961,889

TRACTOR LOADERS Original Filed Sept. l0, 1956 16 Sheets-Sheet 4 INVENTOR.

Nov. 29, 1960 T. G. GRANRYD 2,961,889

TRACTOR LoADERs original Filed sept. 1o, 195e 16 sheets-sheet 5 IN VEN TOR.

BYfMQO @ff Nov. 29, 1960 T. G. GRANRYD 2,951,889

TRACTOR LOADERS Original Filed Sept. 10, 1956 16 Sheets-Sheet 6 IN VEN TOR.

www

Nov. 29, 1960 T. G. GRANRYD TRACTOR LoADERs 16 Sheets-Sheet 7 Original Filed Sept. l0, 1956 www@ NOV. 29, 1960 T. G. GRANRYD 2,961,889

TRACTOR LoADERs original Filed sept. 10, 195e 16 sheets-sheet a y 239 I INVENToR.

Jay/amava PM @W Nov. 29, 1960 T. G. GRANRYD 2,961,889

TRACTOR LoADERs 16 Sheets-Sheet 9 Drginal Filed Sept. 10, 1956 Nov. 29, 1960 T. G. GRANRYD TRACTOR LoADERs 16 Sheets-Sheet 10 Original Filed Sept. 10, 1956 CMAQ Nov. 29, 1960 T. G. GRANRYD 2,961,889

TRACTOR LoADERs Original Filed Sept. l0, 1956 16 Sheets-Sheet 11 l f @64 430 4P@ JNVENTOR.

Nov. 29, 1960 vT. G. GRANRYD TRACTOR LOADERS Original Filed Sept. 10, 1956 16 Sheets-Sheet 12 Nov. 29, 1960 T. G. GRANRYD 2,961,889

TRACTOR LoAnERs original Filed sept. 1o, 1975s 16l Sheetsheet 13 f6. 72- za- 742 '7; 76- 436. & y@ m 4,73 ,ggg' w 1 445" 4 ///W WA V V sa E. #aan 2 s -mi-wr- Tg R515' 58 4196 a? 4421.2 Mas@ 237 'W3 ze? 4428 Y IRE? 71 ggg @82 /g gp 458 l -463 479 l ZZ/- W9 46:2 466* ggg s 4.519 l 460 Z l j .1 @es gg /V /f A/ N MGM( Nov. 29, 1960 T. G. GRANRYD TRACTORLOADERS Original Filed Sept. 10, 1956 16 Sheets-Sheet 14 16 Sheets-Sheet 15 T. G. GRANRYD TRACTOR LOADERS 4L@ 47j M2 INVENToR.

L() ABWL/L95 Nov. 29, 1960 original Filed'sept. 1o. 195e 16 Sheets-Sheet 16 Original Filed Sept. 10, 1956 Q MW W/ A bei@ a W C .IHMYQK @y w nj/w /M /m .y w W WIM l 1 w M l I9 M M m 4 w mi y w TRACTOR LOADERS Thorvald G. Granryd, Libertyville, Ill., assigner to The Frank G. Hough Co., a corporation of Illinois Original application Sept. l0, i956, Ser. No. 608,909,

now Patent No. 2,S42,273, dated July 8, 1958. Divided and this application ct. 17, 1957, Ser. No. 696,897

6 Claims. (Cl. 'M -472) This invention relates generally to tractor loaders, and more specifically to improved transmission and hydraulic means for driving the traction wheels of the loader and for operating the hydraulic systems thereof, and to novel control means for controlling the various functions of the loader. This invention is a division of my previously liled application Serial No. 608,909, tiled September 10, 1956, now Patent No. 2,842,273, for Tractor Loaders.

Tractor loaders as generally known in the art comprises a tractor of either the four wheel rubber tired type or the crawler-track type, and tool means carried by the tractor, and operated by an operator from an operators station in the tractor for performing various material handling functions such as digging, carrying and dumping of different materials. The tractors generally co-mprise some type of power plant such as an internal combustion engine, transmission means, and hydraulic means. The power plant or engine is connected to the input of the transmission means through some clutching means, and the output of the transmission means is connected to the traction members which may be wheels o or crawler-tracks. Additionally, some means for ypower take-off from the engine is provided for driving the necessary hydraulic pump, which in turn delivers the hydraulic fluid under pressure used for operating the tool means of the loader. Thus, it may be seen that the available power of the engine or power source is divided between the traction members and the tool means through the transmission and the hydraulic pump. The methods and constructions for dividing this available engine power as presently known in the art, all have one common disadvantage. This disadvantage arises from the fact that a tractor loader as compared to other vehicles and material handling equipment is used or operated in a unique manner. The power consumed by the traction members and the tool means is rarely used completely separately and at different times. In the usual operation of tractor loaders, power is consumed by both the traction members and the tool means at the same time. A common operation is to operate the traction means to move the tractor so that the tool means engages the material being worked while operating the tool means to work the.

material in some manner. As soon as the traction members meet with some resistance, a condition which is common in digging, a torque reaction is applied from the traction members to the engine through thertransmission. This torque reaction will act as a brake upon the engine causing it to slow down and reduce the power which it develops. Under certain conditions the engine may be completely stalled. Now as the engine output is reduced by the torque reaction from the traction members, the portion of the engine power delivered to the tool means is also reduced so that at these critical times in the operation of the loader, the entire efficiency thereof is drastically reduced. The obstruction or resistance `encountered by the traction members results in a lowered etliciency of the tool means, so that often times the tool means will have insuicient power to operate and relieve ice the obstruction from the traction members. The converse of this is also true. Many times in the operation of these tractor loaders the tool means, while working somev material, will meet an obstruction causing a torque reaction to be applied from the tool means to the engine of the tractor, which torque reaction will reduce the power output of the engine. Again, this point in the operation of the loader generally coincides with the point at which power is being supplied to the traction members and maximum power thereat is desirable in order to maintain high tractive eliort at the traction members so that the traction members may aid the tool means in overcoming the obstruction or working of the material. However with the reduced power output of the engine, less power is supplied to the traction members.

Power plants as used in tractor loaders are generally so designed that at or near the governed speed, maximum engine power is available, and the highest eiciencies for any one-sized loader are produced when the power plant is operated at the governed speed.

These ineiciencies produced in the operation of loaders as now known in the art may be more clearly seen if one specific example thereof is considered. Considering a tractor of either the four-wheel rubbertired type or the crawler-,track type having an internal combustion engine developing a certain maximum power at full throttle governed speed. Further considering that the engine is connected to a transmission through some clutching means such as a torque convertor, and that the transmission is in turn connected to drive the wheels or tracks of the tractor. Additionally, considering the tool means to be a shovel mechanism mounted forwardly of the tractor and operatively connected with the tractor through hydraulically operated boom and linkage means, and a continuously operated hydraulic pump mounted so as to be driven by a power take-oft shaft from the engine. In a normal digging operation of this considered loader, the shovel mechanism is indexed in a dig position, and the transmission then operated to cause the engine to drive the wheels or tracks of the tractor in a forward direction. The tractor will thus force the shovel mechanism into the material to be dug somewhat filling the shovel. While `the wheels or tracks are urging the seovel into the material being dug, the hydraulic means are operated to tilt Athe shovel rearwardly to retain a heaping load within the contines of the shovel. The shovel may also be raised through the material being dug in a scooping action. The loaded shovel is then held in the carrying position and transported to some remote position for dumping, whereupon the loader may again return to the material being dug to repeat the cycle. It thus may be Vseen that at the critical portion of the cycle, that in which both tractive effort and hydraulic power are required for maximum material handling effort, a loader arrangement such as described is Very inefcient. When both the tractive effort and the hydraulic operation is required at the same time as in the digging function, a torque reaction through the hydraulic pump causes a reduction in the speed of the engine and its power output to the traction members with a corresponding decrease in tractive effort at the traction members, and conversely a torque reaction from the traction members will reduce the speed of the engine to cause a corresponding decrease in the speed of the hydraulic pump.

The power trains of tractor loaders presently known in the artlhave further inherent ine'iciencies and disadvantages for example, it is peculiar to the tractor loader art that the transmission should be so constructed that a shift to the various speeds in the reverse direction will result in an overdrive ratio. This is advantageous in that tractor loaders when in the reverse direction are generally not engaged in the working of any material,

but are being moved in preparation for digging operations in the forward direction. Since the load on the tractor loader is then at a minimum and since preparations for actual working operations should be done in a rapid manner, an overdrive ratio in reverse is desirable. These desirable ratios for a tractor loader 'may be produced by transmissions known in the art today, however, the resulting transmissions are then quite cumbersome Aand expensive and amount to little more than -compromise arrangements.

As the tractor loader art has advanced, the use of power shift transmissions with torque convertors between the transmission and the engine have been made. These arrangements have one important disadvantage which results from the torque convertors inability to substantially completely absorb the momentary shock produced in shifting of the transmission. This shock is transmitted to the traction elements and, of course, felt by the operator of the loader. Another disadvantage has been that the tractor loader will creep or drag slightly when the transmission is in one of the driving positions and even when the engine is operating at its lowest speed.

It is an object of the present invention to produce power train means from lan engine to the traction members and to the hydraulic system of a tractor loader which will overcome the ineliiciencies and disadvantages known in tractor loaders presently used in the art today and to provide an arrangement which will substantially fulll the unique requirements of tractor loaders.

It is another object of the present invention to provide a planetary type transmission in which all of the elements of each planetary set is identical in size to the corresponding elements of every other planetary set, and to produce speed ratios which are ideal ratios for a tractor loader.

It is another object of the present invention to provide means in a tractor loader for driving the hydraulic system and for driving the traction members simultaneously, and so that a torque reaction from either the hydraulic system or the traction members increases the torque output to the other.

It is another object of the present invention to provide in a tractor loader having a single engine or power source, a power divider which will divide the available engine power between the traction members and the hydraulic system so that the loading of either one of the hydraulic system or the traction members does not result in a decreased output of the engine but produces a greater engine torque in the other member.

It is another object of the present invention to provide a power shift transmission cooperating with a power divider so that any sudden change in direction or ratio of the transmission will not result in any shock transmitted to the traction members.

It is another object of the present invention to provide means in a tractor loader whereby the full engine power is easily selectively transmitted to either the hydraulic system or the traction members.

It is a further object of the present invention to provide a tractor loader having a hydraulic system wherein power is divided between the traction members and the hydraulic system so that the hydraulic pump of the hydraulic system is rotated intermittently and only as required.

It is another object of the present invention to provide in a tractor loader, a planetary set power divider connected to the engine with one of the members of the planetary set driving the hydraulic system for the loader and with another one of the members of the planetary set driving the traction members of the loader.

It is another object of the present invention to provide in tractor loader, a planetary set power divider wherein one member of the planetary set delivers power to a transmission and another member delivers power to the tractor hydraulic system, and wherein the transmission comprises a plurality of planetary sets of the same size as the power divider planetary set and wherein speeds produced at the traction members are ideally suited for tractor loaders.

It is another object of the present invention to provide a planetary set power divider connected to a tractor engine with one member of the planetary set driving the hydraulic system for the loader and with another member of the planetary set supplying power to the traction members of the loader and wherein the hydraulic system supplies a torque reaction at least as great as the corresponding torque delivered to the traction members and wherein the traction members supply a torque reaction directly proportional to the torque supplied to the hydraulic system.

It is another object of the present invention to provide a planetary set power divider in a tractor loader with one member of the planetary set driving the traction members and with another member of the planetary set driving the main hydraulic pump for the hydraulic system of the loader, and further wherein a throttle sensitive pressure regulating valve is provided for applying a regulating lforce upon the main hydraulic pump of a vmagnitude dependent upon the throttle setting.

vIt is another object of the present invention to provide a planetary set power divider in a tractor loader with one member of the planetary set driving the `traction members and with another member of the planetary set driving the main hydraulic pump for the hydraulic system of the loader, and further wherein an engine speed sensitive pressure regulating valve is provided for applying a regulating force upon the main hydraulic pump of a magnitude dependent upon the speed of the engine.

It is another object of the present invention to provide a tractor loader with a planetary set power divider wherein one member of the planetary set drives the traction members through a transmission and wherein a novel control arrangement cooperates with the transmission to provide a brake for that member of the planetary set to lock the rtraction members against movement.

It is a further object of the present invention to provide a transmission for a tractor loader which will fulll the ideal ratio requirements for a tractor loader and which is formed of a plurality of planetary sets to provide a forward and reverse direction in two dierent speeds. It is a further object to provide such a transmission with means for easily converting it to a three-speed forward and reverse direction transmission, and further such that the intermediate speed ratio will split the difference ratio between the low and the Vhigh speed equally, in other words, that for the particularly-sized planetary set the three used ratios from low to high will form an exact geometrical series.

It is another object of the present invention to provide a planetary set power divider wherein one member of the planetary set drives the traction members through a transmission and another member of the planetary set drives a hydraulic system, and having control means operating to substantially remove any torque reaction from the member of the planetary set driving the hydraulic system whereby the tractor will not creep when the transmission is operated to one of the speed ratios and the engine is operating at its lowest speed.

A further object of the present invention is to provide a tractor loader with a transmission and a hydraulic system connected to the engine so that the transmission is operable to one position to provide a direct drive between the engine and the hydraulic system.

A further object of the present invention is the provision in a tractor loader of a power divider simultaneously driving the main hydraulic pump and the transmission for the tractor with the power divider so constructed that the main hydraulic pump performs the function of a shock absorber for the transmission as the transmission is operated through its dierent speed ratios and directions.

A further object of the present` invention is to provide a simple and efficient control system for the different load conditions encountered in a tractor loader having a single engine driving a planetary set power divider in turn simultaneously driving a main hydraulic pump and the traction members of the tractor.

Other objects and the features of the present invention will be apparent upon perusal of the following specification and drawings of which: i

Figure 1 is a top plan view of one embodiment of a tractor loader constructed according to the present invention;

Figure 2 is a side elevational view of the tractor loader shown in Figure l;

Figure 3 is an enlarged side elevational view partially in section of the tractor portion of the tractor loader shown in Figures 1 and 2;

Figures 4A and 4B which are intended to be placed side by side for viewing are a cross-sectional view of the transmission and power divider elements of the present invention; and taken along a line such as line 4 4 of Figure 6;

Figure 5 is a cross-sectional view of the power divider element of the present invention as taken substantially along a line such as line 5-5 of Figure 4A;

Figure 6 is a cross-sectional view of the transmission portion of the present invention and is taken along a line such as line 6-6 of Figure 4B;

Figure 7 is a diagrammatic View of the various elements of the present invention particularly showing the hydraulic interconnections of the various elements;

Figure 8 is an enlarged cross-sectional view of one of the elements shown in Figure 7;

Figures 9, 10, and l1 are also enlarged cross-sectional views of different ones of the elements shown in Figure 7;

Figure 12 is another enlarged cross-sectional view of one of the elements shown in Figure 7 and with that element operated to one of its twelve possible-operated positions;

Figures 13 through 23 are views substantially identical to Figure 12 except that the valve spools are shown in the other eleven operated positions; and

Figure 24 is a graph showing how the engine power is divided in the present invention between the traction members and the hydraulic system.

The present embodiment is a preferred embodiment but it is to be understood that changes can be made in the present embodiment by one skilled in the art without departing from the spirit and scope of the present invention.

General description For a general description of the present invention reference is made to the drawings. The present embodiment comprises a tractor 10 of the four-wheel rubber tired type with all of the wheels being driven, and a shovel arrangement 11 operatively mounted on the tractor 10 to extend forwardly thereof as can be seen in Figures 1 arid 2. Considering Figure 3 it may be seen in the enlarged cutaway of the tractor 10, that the tractor 10 is provided with an engine 12 mounted in the rearward portion and with certain drive and control means. The flywheel housing 13 is directly mounted to the engine 12 and includes the output shaft thereof. The power divider 14 is mounted to the ywheel housing 13. To the power divider 14, the transmission 15 and the main hydraulic pump 16 are mounted. The transmission 15 includes a transfer drive case 17 carrying the output of the transmission 15 to the traction members. From the transfer drive case 17, appropriate shafts 1-8 and 19 deliver power through conventional universal joints and differential assemblies to the rear and front wheels respectively of the tractor 10. A hydraulic pressure compensating and regulating valve or main control valve 2.0 connected to the output of the main hydraulic pump 16 delivers hydraulic fluid under proper pressures to the tool means hydraulic control valve 21. Operation of the tool means hydraulic control Avalve 21. through the levers 30 and 31`by the operator 1n the operators compartment causes the desired operation of the tool means. A hydraulic uid reservoir V22 Vis also provided for the hydraulic systems. To provide proper hydraulic control pressures, about p.s.i. in

fthe present embodiment, for operating the transmission 15, and to provide an engine speed responsive valve for the main control valve 20, a governor valve and hydraulic pump assembly 23 is provided. The governor valve and hydraulic pump assembly 23 is mounted to the crankshaft of the engine 12 at the opposite end thereof from the iywheel housing 13. The hydraulic pump portion of assembly 23 delivers hydraulic fluid to the main control valve 20 through the governor valve portion of assembly 23, the ltransmission control valve 24, and the secondary control valve assembly 25. The transmission control valve 24 is mounted on the side on the transmission 15 and is operated by the operator of the tractor through appropriate linkage and leverage arrangements. The secondary hydraulic valve assembly 25 has a plurality of functions which will be described in detail below.

For the general description it may be stated that the secondary hydraulic valve assembly 25 regulates hydraulic fluid pressures for operation of the transmission 15, for the lubrication oil for the system, and for a portion of the main control valve 20.

The flywheel housing 13, the power divider 14, the transmission 15 and the main hydraulic pump 16 may be seen in section in Figures 4a and 4b. Generally it may be stated that the power divider 14 comprises a planetary set wherein the output shaft of the engine 12 is connected to one of the members thereof, and the inputs of the main hydraulic pump 16 and the transmission 15 are connected to the other members of the planetary set. The transmission 1S is of the type wherein a plurality of planetary sets provide the various desired speed ratios through the operation of disk type brakes. Each component of each planetary set in both the transmission 15 and lthe power divider 14 is of an identical size with the comparable member of each of the different planetary sets. The basic portion of the transmission 15 is a twospeed transmission giving a low or creeper speed in one ratio and a high or travel speed in the other ratio. The basic portion of the transmission 1S is modified by a simple attachment which produces a third or intermediate speed which is exactly midway between the Creeper speed and the travel speed, the three speed ratios forming an exact geometric series. In additional the transmission 15 is operable in either the forward or rearward direction.

Figures 7 shows the complete hydraulic system in a somewhat diagrammatic view. The elements 20, 23, 25, 21 and 24 are then each shown in detail in the remaining ligures excluding Figure 24 which shows an explanatory graph. To make a broad summarization of how the hydraulic system cooperates with the engine 12, the power divider 14, the transmission 15, the traction members, and the tool means, reference is made to Figure 24. Figure 24 shows a chart wherein the power used by the main hydraulic pump and the power used by the traction members are plotted against the total power used on an axis of ordinates and the speed of the traction members on an axis of abscissas, and is based upon the assumption that either the traction members or the main hydraulic pump is capable of using the engine power available at full throttle governed speed. The plot of the power used by the traction members is a straight line beginning at a minimum or zero speed for the traction member and minimum or zero power used to the maximum speed of the traction members at the total engine power available at full throttle governed speed of the engine. The power u'sed by the main hydraulic pump is also a straight line beginning at the minimum or zero speed of the traction member and total engine power available at full throttle governed speed of the engine to the maximum speed of the traction members and the minimum or zero I:wensen Ipower used. The main hydraulic pump is used as a reference lpoint-for the hydraulic system since the power delivered by the main hydraulic pump may be used by elements other than the tool means, for example, in some instances the main control valve 20 may absorb some of the engine power. The traction members are used as a reference point since except for negligible power losses in the Ypower train, the traction members -consume all of the powerdelivered to the transmission 15. From this chant in Figure 24 much can `be seen about the operation 'and .result of the present invention. First, it may be seen that for any one speed of the traction members, the power used by the traction members at that speed plus the power used by the main hydraulic pump at that speed of the traction members equals the total engine power available at full throttle governed. Thus, when the power used by the traction member is at zero, the speed of the traction member is zero and the power used by the main hydraulic pump is the total engine power available at full throttle governedsp'eed. When no power is used or consumed by 4the main hydraulic pump, the power used by the traction members is the total engine power available at full throttle governed speed and the speed of the traetion member is at the maximum. The total engine power available at full throttle governed speed is always divided between the main hydraulic pump and the traction member lin some proportion dependent upon the speed of the traction members. These results may also be interpreted in terms 'of the power available. Considering that with the total engine power available at full throttle governed speed, if for some reason the speed of the traction members is reduced, the power used by the traction members will go down and the power available for use by the main hydraulic pump will go up, and conversely if for any reason the power available to the main hydraulic pump is not used or decreased, the power available for use by the traction members is increased. These unique results are particularly important in the art of tractor loaders. Considering the loader as a four-wheel rubber tire tractor with a hydraulically operated shovel carried by the tractor, if the tractor is operated to move the shovel into a load which is being dug and should the traction members encounter an obstruction so that the speed thereof goes down, for example, to substantially zero, it may be seen that the hydraulic system or the hydraulically operated shovel may then use substantially the total engine power available at full throttle lgoverned speed to permit -a maximum effort in Ithe'u'se of the hydraulically operated shovel to dig, Vpry out or break away any material being dug, because the necessary torque reaction is provided by the traction members, and produces excellent tractive elort -to attempt to overcome the obstruction. Again, conversely, if the hydraulically operated shovel meets with some obstruction or is caught into some load being dug, substantially the total engine power available at full throttle governed speed is then available for use by the traction members so that the tractor may be moved to aid in the earth working operations of the loader. This is a very different result from that achieved by tractor loaders presently used in the art including those using torque convertors. In tractor loaders presently used in the art, if the :traction members should strike an obstruction, this is applied as a reaction force to the engine, which due tothe reactive torque is retarded. The retarding of the engine causes a corresponding power loss to the hydraulic system of the shovel mechanism. The same is true if the shovel mechanism strikes an obstruction.

Tractor and shovel arrangement Other advantages and new features of the present inv ention will be described in the following detailed description of the present invention for which reference is first made to Figures 1, 2, and 3. The tractor 10 of the present embodiment has traction members comprising four wheels 26. The wheels-26 support .the framell, `to which the ly connected to the inner end of the control 32.

l8 various rcomponents of the tractor are mounted. The engine 12 is disposed within the body o'f the tractor upon the iframe 27 at the rearward portion of the tractor 10. An operators compartment 28 mounted within the body of the tractor and positioned forwardly of the engine 12 -includes a steering wheel 29 and the various necessary operating controls 31, 32 and 33. Controls 30 and 31 are the operating levers of the valve 21 for controlling the Operation of the hydraulic tool means. 4Control 32 comprises a lever pivotally mounted within a tubular member 34. Tubular member 34 is operatively connected to spool 35 of the transmission control valve 24 through a linkage arrangement 36 so that when the control 32 is rotated about the longitudinal axis of the tubular member 34, the valve spool 35 is moved to its various operative positions. A rod 37 is mounted within the tubular member 34 for a sliding movement along the longitudinal axis thereof. The upper end of the rod 37 is pivotal- The lower end of the rod 37 is pivotally mounted to one arm of a bellcrank 38. The bellcrank 38 is pivotally mounted in the body of the tractor 10, and the other end of the bell'crank 3S lis operatively connected to the valve spool 39 of the transmission control valve 24 through a linkage arrangement 4t), so that when 'the control 32 moves in an upward and downward direction, the valve spool 39 is moved to its various operative positions. The control 33 is afoot throttlepedal and is pivotally mounted on the floor of the operators compartment 28. The throttle pedal 33 is operatively connected through a linkage arrangement :41 with the throttle control 42 on the engine and a lever mounted in the hydraulic valve 25. As the throttle pedal 33 is depressed and raised the throttle control 42 is opened and closed. The cooperation of the linkage arrangement 41 with the control valve 25 will be described below.

The earth-working tool means or shovel mechanism 11 of the present invention may be of any suitable type. In the present embodiment, the shovel mechanism 11 comprises `a bo'orn 44 pivotally mounted on the tractor 10. The boom 44 comprises a pair of boom arms one of which is positioned on each side of the tractor 10 and extends forwardly thereof. To raise and ylower the boom 44, a pair of hydraulic rams 45 are provided. `Each of the hydraulic rams 45 are vpivotally mounted at one end thereof tothe tractor 10 on one side of tractor 16 with the other end of each of the hydraulic rams 45 pivotally connected t0 one of the boom arms of the boom 44 intermediate the ends thereof. Thus it may be seen that as the hydraulic rams 45 are extended and contracted, the boom 44 is raised and lowered. A bucket or shovel 46 is carried by the forward end of the boom 44. The shovel 46 is pivotally mounted through suitable brackets on the rear side thereof to the outer or forward ends of each of the boom arms of the boom 44. To position and pivot the shovel 46 relative to the boom 44, an adjustable linkage arrangement is provided. This adjustable linkage arrangement is formed Vin portions disposed at each side of the tractor 10. VEach of the portions of the adjustable arrangement comprises a hydraulic ram 47, a lever 48 and a link 49. Each of the levers 48 is pivotally mounted intermediate its ends within one of the boom arms of the boom 44 intermediate the ends thereof. The lower end of each of the levers 48 is pivotally mounted to one end of the links 49. The other end of each of the links 49 is pivotally mounted to the rear surface of the shovel 46 through suitable brackets secured thereon. The upper end of each of the levers 48 is pivotally connected to one end of one of the hydraulic rams 47. The other end of each of the hydraulic rains 47 is pivotally connected to the tractor 10. Thus it may be seen that as the hydraulic rams 47 are extended and contracted, the levers 4S are pivoted to in turn move the links 49, to cause the bucket 46 to be positioned and pivoted relative to the boom 44. The operation of these tractor loaders such as herein defined are well .known .in the art. They are 

